EP2663823A1 - Wärmeübertrager - Google Patents
WärmeübertragerInfo
- Publication number
- EP2663823A1 EP2663823A1 EP12700478.6A EP12700478A EP2663823A1 EP 2663823 A1 EP2663823 A1 EP 2663823A1 EP 12700478 A EP12700478 A EP 12700478A EP 2663823 A1 EP2663823 A1 EP 2663823A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- fluid
- dip tube
- refrigerant
- channel
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims abstract description 103
- 238000007599 discharging Methods 0.000 claims abstract description 14
- 238000007654 immersion Methods 0.000 claims abstract description 10
- 239000003507 refrigerant Substances 0.000 claims description 62
- 239000002826 coolant Substances 0.000 claims description 20
- 238000001816 cooling Methods 0.000 claims description 16
- 238000007789 sealing Methods 0.000 claims description 9
- 229910000679 solder Inorganic materials 0.000 claims description 9
- 238000007667 floating Methods 0.000 claims description 8
- 238000004378 air conditioning Methods 0.000 claims description 6
- 238000010438 heat treatment Methods 0.000 claims description 6
- 238000010276 construction Methods 0.000 claims description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 5
- 239000000853 adhesive Substances 0.000 claims description 2
- 230000001070 adhesive effect Effects 0.000 claims description 2
- 210000001050 stape Anatomy 0.000 claims 1
- 238000005476 soldering Methods 0.000 description 14
- 238000000034 method Methods 0.000 description 6
- 238000003860 storage Methods 0.000 description 4
- 230000002528 anti-freeze Effects 0.000 description 3
- 238000005304 joining Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 229910052751 metal Inorganic materials 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 239000003570 air Substances 0.000 description 2
- 239000012080 ambient air Substances 0.000 description 2
- 238000007747 plating Methods 0.000 description 2
- 241000251468 Actinopterygii Species 0.000 description 1
- 235000002568 Capsicum frutescens Nutrition 0.000 description 1
- CWYNVVGOOAEACU-UHFFFAOYSA-N Fe2+ Chemical compound [Fe+2] CWYNVVGOOAEACU-UHFFFAOYSA-N 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000004026 adhesive bonding Methods 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 238000000889 atomisation Methods 0.000 description 1
- 238000005253 cladding Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000008021 deposition Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- -1 for example Substances 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 108090000623 proteins and genes Proteins 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000010792 warming Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/022—Evaporators with plate-like or laminated elements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3227—Cooling devices using compression characterised by the arrangement or the type of heat exchanger, e.g. condenser, evaporator
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3229—Cooling devices using compression characterised by constructional features, e.g. housings, mountings, conversion systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
- F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
- F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
- H01M10/61—Types of temperature control
- H01M10/613—Cooling or keeping cold
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
- H01M10/62—Heating or cooling; Temperature control specially adapted for specific applications
- H01M10/625—Vehicles
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
- H01M10/66—Heat-exchange relationships between the cells and other systems, e.g. central heating systems or fuel cells
- H01M10/663—Heat-exchange relationships between the cells and other systems, e.g. central heating systems or fuel cells the system being an air-conditioner or an engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/18—Optimization, e.g. high integration of refrigeration components
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
- F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
- F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/10—Energy storage using batteries
Definitions
- the invention relates to a heat exchanger according to the preamble of claim 1, a system for a motor vehicle for heating and / or cooling a battery according to the preamble of claim 14 and an automotive air conditioning system according to the preamble of claim 15,
- Batteries of hybrid or electric vehicles must be heated or cooled to maintain a sufficient operating temperature of the battery, for example in a temperature range between 0 ° C and 40 ° C.
- the battery When removing or charging electrical energy from the battery, the battery releases heat, so the battery must be cooled to prevent it from warming to temperatures in excess of 30 ° C or 40 ° C.
- a heating of the battery At low outside temperatures, for example, below 0 ° C, a heating of the battery is required so that etechnischmaschinezzle energy can be removed from the battery as well as a charge of electrical energy is possible.
- the hybrid or electric vehicle has a coolant circuit with which the battery can be cooled and preferably heated.
- DE 101 28 164 A1 shows a vehicle cooling system for an electric or hybrid vehicle.
- the vehicle cooling system includes a coolant circuit that is thermally coupled to a battery.
- an evaporator of a refrigeration circuit with a condenser, a compressor and an expansion valve is also installed in the coolant circuit with the battery.
- the coolant circuit can be cooled with the battery, so that by means of the refrigerant circuit and the battery can be cooled.
- a plurality of plates are stacked parallel to each other in the vertical direction as a heat exchanger in plate or disc construction. Between the plates, a first flow space for refrigerant forms as a first fluid and a second flow space for a second fluid, so that heat can be transferred from the second fluid to the refrigerant.
- DE 95 23 475 C1 shows a plate heat exchanger, in particular oil cooler with a stack of heat exchanger plates, which lie to form separate flow channels for the heat-exchanging media into each other and are connected by joining technology and in which the inlet and outlet ports for at least one medium on the same Side of the plate stack lie, with provided in the inlet and outlet channels inserts for flow deflection in meandering, wherein the one insert the one inlet and outflow substantially blocks and the other use the other inlet or outflow channel partially covers.
- cladding wherein the inserts are made as a single injection molded part, which are connected by a connecting part and that the inserts are releasably secured in the inflow and in the outflow.
- EP 2 107 328 A1 shows an evaporator, in particular for a motor vehicle, comprising a plurality of plates stacked parallel to each other in a vertical direction with aligned apertures for supplying and discharging a first fluid and a second fluid designed as a refrigerant, wherein between two adjacent plates a flow channel of the first type for guiding the first fluid in alternation with a flow channel of the second type for guiding the second fluid are formed, wherein a heat transfer surface of the plates has a length in the flow direction of the refrigerant and a perpendicular thereto width, wherein the ratio of the length to the Width is not greater than about 1, 3.
- Disk heat exchangers or chillers are used in systems to cool the batteries of hybrid or electric vehicles with a cooling circuit.
- the heat exchanger or chilier is constructed in a disk construction and comprises a multiplicity of stacked stacked disks, so that a first fluid channel for the coolant and a second fluid channel for the coolant, for example water with an antifreeze center, are formed between the stacking disks.
- the refrigerant is thereby passed through at least two, preferably at least three, sections of the first fluid channel between the stack disks in the opposite direction, that is meandering, through the first fluid channel between the stack disks.
- the first inlet port and the first outlet port for the refrigerant is formed at different opposite sides of the heat exchanger, for example, the I / 'n iassö réelle on the cover plate and the outlet opening to a bottom plate.
- Such heat exchangers are also provided with a thermal expansion provided onsventii.
- the refrigerant introduced into the heat exchanger is controlled in its flow rate depending on the temperature of the effluent from the heat exchanger refrigerant, for example by the flow cross-sectional area of an inflow channel is controlled at the expansion valve in dependence on the temperature at which the refrigerant from the Heat exchanger flows out.
- the thermal expansion valve thus requires both an inflow, which is preferably variable in the flow cross-sectional area » and an outflow, through which the discharged from the heat exchanger refrigerant is passed, so from the thermal expansion valve, the temperature of the effluent from the heat exchanger refrigerant to the outflow channel Expansionsventtls can be detected. If the inlet and outlet openings for the refrigerant are formed at two opposing sides on the heat exchanger, it is necessary that the refrigerant exiting at the outlet opening be conducted in a terminal manner to the thermal expansion valve with a pipe if the thermal expansion valve is in the range, for example the inlet opening and the Abdeckplaite is formed.
- the heat exchanger or evaporator with the thermal expansion valve requires a large installation space due to the pipe in order to conduct the refrigerant from one side of the heat exchanger to another side of the heat exchanger with the thermal expansion valve.
- the object of the present invention is to provide a heat exchanger, a system for a motor vehicle for heating and / or cooling a battery and a Kraft2165! Age available, in which the heat exchanger requires a small space and simple and inexpensive to manufacture is.
- a heat exchanger or chili wheel in disk construction comprising a plurality of stacked stacked disks, so that between the stacking disks, a first fluid channel for a first fluid and a second fluid channel for a second fluid is formed, the stacking discs first openings as the first fluid channel for supplying and discharging the first fluid, the stacking disks having second openings as a second fluid channel for supplying and discharging the second fluid, at least one deflecting device closing at least one first opening, so that the first fluid meanders through at least two, preferably at least three, Sections of the first fluid channel between the stacking disks is guided in the opposite direction through the heat exchanger, a first inlet and outlet opening for input and output of the first fluid, a second
- the refrigerant is passed through at least two, preferably at least three, portions of the first fluid channel between the stack disks meandering in the opposite direction. If the first fluid in the first fluid channel between the stack disks has a high flow velocity, for example, if three sections are formed, the sum of the flow cross-sectional areas of the first fluid channel between all the stack disks is only one third of the sum of the flow cross-sectional areas of the first fluid channel between the stack disks , As a result, a large heat transfer from the first fluid to the second fluid is made possible with the heat exchanger even with a small space or vice versa due to the large or larger flow rate of the first fluid.
- the first inlet or outlet opening for the first fluid is formed by a dip tube, so that the first inlet and outlet opening for the first fluid on the same side of the heat exchanger, for example! only on the cover plate or only on a bottom plate is formed.
- a thermal expansion valve to the heat exchanger in a complex manner with a pipe to discharge the effluent from the heat exchanger refrigerant from one side of the heat exchanger to another side of the heat exchanger with the thermal expansion valve , As a result, space can be saved and the cost of producing the heat exchanger can be reduced.
- the dip tube is insoluble, in particular stoffscWüss ⁇ g, z. B. as a solder or adhesive bond, connected with the heat exchanger and / or through the dip tube, the first fluid at a distance (to the inlet or outlet) in the first fluid channel can be introduced.
- the distance refers only to the one or the first iassö réelle, which is formed by the dip tube.
- the heat exchanger is an evaporator and the first fluid is a refrigerant and the inlet port is formed by the dip tube; but not the opening.
- One end of the dip tube forms the inlet or outlet port for the first fluid, and the distance is the distance from the inlet or outlet port to at least one flow port on the dip tube.
- the immersion tube penetrates the at least one deflection device so that the light guided through the dip tube first fluid is Maschinenlei 'TBAR through the at least one redirector.
- the at least one deflection device as a deflection plate or a separate sealing element, for. B, sealing plate, formed.
- a deflecting disk is designed, for example, as a stacking disk, which has only a first opening instead of two openings, so that thereby the first fluid is diverted in the space between the corresponding first openings and thereby meandering through the first fluid channel between the stacking disks in the opposite direction ,
- a separate sealing element for example a sealing plate or a sealing lip, thereby completes a first opening of the stacking disk, thereby completing a first opening with an additional component on the stacking disk
- the at least one flow opening is formed in the region or at the other end of the dip tube with respect to a first end of the dip tube with the first input or Austessö opening.
- the at least one flow opening is formed radially and / or axially with respect to a longitudinal axis of the dip tube.
- the heat exchanger is designed as an evaporator with a, preferably thermal, expansion valve and the first fluid is a refrigerant and the second fluid is a coolant, for. As water or air.
- the thermal expansion valve has both an inflow channel for introducing the refrigerant and an outflow channel for discharging the refrigerant.
- the thermal expansion valve further preferably comprises a device for changing the flow cross-sectional area of the inflow channel in dependence on the Temperature of the guided through the discharge channel to the expansion valve refrigerant.
- the expansion valve is fastened to the remaining heat exchanger with a connecting flange and the connecting flange has both an inflow channel for introducing the refrigerant and an outflow channel for discharging the refrigerant.
- the expansion valve preferably directly, without a connecting flange to the other heat exchanger, for example, on a cover plate or on a bottom plate, attached.
- a connecting flange outlet opening and the outflow channel of the connecting flange are formed in alignment with the first outlet opening on the remaining heat exchanger and / or the Ausstrcmkartai has at the Vecbindunqsttansch substantially no deflection.
- substantially no deflection means that the outflow channel does not have a bend or curve for deflecting the refrigerant or the first rudder with a deflection of at least 20 ", 10 °, 5 ° or 2.degree ..
- the dip tube with a non-locating bearing and a fixed bearing is attached to the heat exchanger, and at the floating bearing the dip tube is in the direction of the longitudinal axis of the dip tube
- the heat exchanger or the stack from the stacking disks is connected to one another in a material-locking manner with soldering during a soldering process in a soldering oven a setting process of the stacked stacking disks, thereby decreasing the size of the stack perpendicular to a plane defined by the stacking disks.
- the dip tube is already arranged on the heat exchanger or within the stack and is also firmly bonded to the heat exchanger at the fixed bearing.
- a floating bearing is required so that the stack can perform the setting process during the soldering process.
- the fixed bearing is formed on the cover plate and the dip tube is connected by means of a Lotplatt réelle on the cover plate and the dip tube during soldering in the soldering furnace material with the cover plate.
- the floating bearing is formed on the deflection plate.
- the deflection plate has an opening through which the dip tube is performed.
- the heat exchanger comprises a fixing device for fastening the heat exchanger and preferably the fixing device is formed by the connecting flange.
- the fixing device can also be designed as an additional component in addition to the connecting flange or the connecting block. For example, such a fixing device is firmly bonded with soldering to the cover plate or to the bottom plate.
- the fixing device as a separate component or as a connection flange at least in this case has one, preferably several, holes on and in these holes can Befestig ungseiemente, for case '- game screws or bolts, be secured to fix the IQ heat exchanger on another component, for example a body of a motor vehicle,
- the ratio between the flow cross-sectional area of the dip tube and the flow cross-sectional area of a first opening outside the dip tube is between 0.1 and 0.6.
- this is preferably Immersion tube formed at the first inlet opening, so that flows through the dip tube, the liquid refrigerant in the heat exchanger or evaporator.
- the mass flow density is thus high in the dip tube, v / eil the refrigerant has not yet evaporated.
- the refrigerant evaporates while passing through the first Fluidka- na !, so that it flows through a first breakthrough outside of the dip tube, the refrigerant is at least already partly evaporates and thereby a lower mass Stromd 'eights has. For this reason, it is required that the size of the flow cross-sectional area of the first aperture outside the dip tube is larger than the flow cross-sectional area of the dip tube.
- the components of the heat exchanger in particular the dip tube, the stacking disks, the cover plate, the bottom plate, the connecting flange and / or the expansion valve at least partially, in particular completely, of metal, in particular steel, iron or aluminum or non-ferrous metal ,
- the components of the heat exchanger are bonded together, in particular by means of soldering.
- the components of the heat exchanger have a plating with solder for the cohesive connection of the components of the heat exchanger by means of soldering in a soldering oven.
- the cover plate and / or the bottom plate have a larger, preferably by at least 1, 5, 2, 3 or 5 times greater thickness than the stacking disks.
- the length of the dip tube is smaller than the extent of the stack perpendicular to a plane spanned by the stacking disks plane.
- the dip tube is circular in cross-section » elliptical, polygonal, z.
- the dip tube has a different flow cross-sectional area in the longitudinal direction, for. With a deviation of more than 5%, 10% or 20%.
- the sum of the flow cross-sectional area of the at least one flow opening of the dip tube is smaller, preferably smaller by more than 5%, 10% or 20%, than the flow cross-sectional area of the dip tube. This leads to a micro-throttling during the outflow of the refrigerant from the dip tube and thus to a better distribution by atomization of the refrigerant as it exits the dip tube.
- Inventive system for a motor vehicle for heating and / or cooling a battery and preferably a motor vehicle interior comprising a coolant circuit for cooling the battery and preferably of the motor vehicle interior, a refrigeration circuit with a condensate tor, a compressor, an expansion vent, preferably a first evaporator for cooling the motor vehicle interior and a second evaporator for cooling the battery by the second evaporator is thermally coupled as a heat exchanger to the coolant circuit and wherein the heat exchanger is designed as a described in this patent application heat exchanger ,
- the stacking disks of the heat exchanger are expediently arranged to form a stack of stacking disks stacked on top of one another.
- the stack disks are substantially, for. B, with a deviation of less than 10 °, 5 ° or 2 °, arranged in parallel.
- the heat exchanger comprises at least 5, 8, 10, 20, 30, 38, SO, 56 or 68 staple leads.
- An automotive air conditioning system comprises a system described in this patent application and / or the motor vehicle air conditioning system comprises a heat exchanger described in this patent application.
- Fig. 1 is a perspective sectional view of a heat exchanger
- Fig. 2 is a perspective sectional view of the heat exchanger
- FIG. 5 shows a storage or connection in a first embodiment of a dip tube on a deflection plate
- FIG. 6 shows a bearing or connection in a second exemplary embodiment of the immersion tube on the deflecting disk
- FIG. 7 shows a bearing or connection in a third exemplary embodiment of the tug-of-a-tricycle on the deflecting disk
- FIG. 10 shows a bearing or connection in a sixth exemplary embodiment of the dip tube on the deflecting disk.
- FIG. 1 in a side view heat exchanger 1 or chiller 1 is used in a system, not shown, for heating and / or cooling a battery of a motor vehicle as a hybrid or Bektrofa rzeug.
- the heat exchanger 1 is used as a heat exchanger 1 in
- a large number of stacking disks 2 with first th and second openings 4, 5 and openings 4, 5 are stacked on top of each other to form a stack 3.
- a first fluid channel and a second fluid channel for passing a fluid are formed between the stacking disks 2. This allows heat to be transferred from the first fluid to the second fluid or vice versa.
- the first openings 4 likewise form the first fluid channel, through which the first fluid flows into and out of the first fluid channel between the stacking disks 2. This also applies analogously to the second fluid channel or the second openings 5.
- the cover plate 9 also has first openings 4 or openings and second openings 5 or openings 5 for passing the first and second fluids.
- the two first openings 4 are hereby integuch on the Abdeckglatte 9 and not formed on the bottom plate 10, so that the two first openings 4 are formed on one side of the stack 3.
- a first opening 4 forms a first inlet opening 6 for the first fluid, in this case refrigerant, and a further first opening 4 on the cover plate 9 forms a first outlet opening 7 for the refrigerant.
- a second inlet opening 8 (FIG. 3) and a second outlet opening (not illustrated) on the cover plate 9 form the inlet and outlet opening 8 for the second fluid.
- the second fluid is passed through the second fluid channel between the stacking disks 2 without deflection and not meandering in only one direction of flow through the second fluid channel.
- this attachment of the dip tube 11 to the cover plate 9 is a fixed bearing 15 for the dip tube 11.
- the refrigerant is meandered through the first Fluidkanai between the stacking disks 2 by three sections 25 in the opposite direction through the first Fluidkanai between the stacking disks 2 is this it is necessary that the first openings 4 of the Stapeilotn 2 are closed in two places.
- two stacking disks 2 have no first openings 4 and thus form a deflection disk 24 as a deflection device 23, in FIG. 1, a lower deflection disk 24 is provided on the left first openings 4 shown in FIG. 1, which separates the left first openings 4 and it is at the right first openings 4, an upper deflection plate 24 is present, which separates the space formed by the right first openings 4 first Fluidkanai at one point the lower deflection plate 24 has an opening through which the dip tube 11 is performed.
- a lower end of the dip tube 1 in this case has an axfate flow opening 12, through which the liquid refrigerant introduced at the first inlet opening 6 flows out of the dip tube 11 into the first fluid channel below the deflection plate.
- the refrigerant flows from left to right through the lowermost portion 25, is then diverted in the first fluid channel in the region of the right first openings 4 and then flows in the opposite direction through the central portion 25 of the first Fluidka- channel , Subsequently, the refrigerant at the left first fürbrechun- gene 4 above the deflection plate 24 and outside of the dip tube 1 1 again diverted and flows through the uppermost portion 25 and then from the uppermost portion 25 in the first Fluidkanai above the upper deflection plate 24 in the right first openings 4 and then from the first outlet opening 7 from the heat exchanger 1 and the stack 3 from the stacking disks 2 again.
- the connection between the dip tube 1 1 and the deflection plate 24 is as a Ager 14 is formed, so that in the direction of a longitudinal axis 13 of the dip tube 11, the dip tube 1 1 is movable to the deflection plate 24 as a floating bearing 14.
- the flow opening 12 of the dip tube 11 is formed axially to the longitudinal axis 13 of the dip tube 1 1,
- a connecting flange 16 and a connecting block 17 is attached from metal by means of a solder joint.
- the connecting flange 16 has an inflow channel 18 for introducing the refrigerant into the heat exchanger 1 and an outflow channel 19 for discharging the refrigerant from the heat exchanger 1.
- the outflow channel 19 is formed in alignment with the first outlet opening 7 and the inflow channel 8 has two bends or curves as deflection points of approximately 90 °.
- a kausflansch- outlet opening 20 is formed as the end of the Ausströmkanals 19 in alignment with the first ⁇ auslassö réelle 7 on a Stapefin 7 and ..
- the connection block 17 is also a fixing device 21 for fixing the heat exchanger 1 to other components, for example a body of a motor vehicle (not shown).
- the fixing device 21 or the connecting flange 16 has a plurality of bores 22. Through these bores 22 (not shown) by means of screws or bolts in the holes 20, a mechanical connection between the fixing device 21 and a primarilyen component can be produced. Notwithstanding the cohesive solder joint between see the connecting block 17 and the cover plate 9, the connecting flange 16 can be fluid-tightly connected to the cover plate 9 with a screw, not shown, and at least one O-ring seal.
- a thermal expansion valve 26 with an inflow 27 and an outflow 28 is attached on the connecting flange 16.
- the expansion In this case, the actuation valve 26 is connected to the connecting flange 16 in a fluid-tight manner, for example with a material-bonded joining connection, for example a laser or plasma welding, a solder connection or another joining method, such as gluing or forming.
- the expansion valve 26 may also be fastened to the connecting flange 16 with a screw or rivet connection, and a fluid-tight connection between the expansion valve 26 and the connecting flange 16 (not shown) by means of at least one 0-ring seal.
- the inlet channel 18 of the connecting flange 16 opens into the inflow channel 27 of the expansion valve 26 in alignment
- the outflow channel 19 of the connecting flange 16 opens into the outflow channel 28 of the thermal expansion valve 26,
- the dip tube 11 has two radial flow openings 12. By the two radial flow ports 12 with respect to the longitudinal axis 13, a refrigerant flows into the first Flu 'idkanal below the deflection disc 29 to the left first perforations. 4
- two coolant nozzles 29 for introducing and discharging the coolant for example, water with an antifreeze are also shown.
- the coolant pipe 29 are aligned with the coolant pipe 24 to the stacking disks 2 second openings 5 are formed.
- the second openings 5 through which the coolant is introduced into the heat exchanger 1 are shown.
- the expansion valve 26 without the connecting flange 16 is attached to the cover plate 9, for example by means of a solder joint. Lassö réelle 7 formed on the stack 3 of stacking disks 2 with the cover plate 9 and the bottom plate 10 as a remaining heat exchanger 1 in alignment with the outflow channel 28 of the expansion valve 26.
- the liquid refrigerant introduced into the expansion valve 28 through the inflow passage 27, after flowing through the inflow passage 27, is directed from the end of the inflow passage 27 to the first intake port 6 and the dip tube 11 through an additional fuel conduit.
- This additional refrigerant pipe as a separate component in this case has a small size or expansion, because no deflection of the refrigerant from one side to another side of the other heat exchanger 1 is required and corresponds in function to the egg ' nströmkanal 18 of the connecting fish 16 according to the first and second embodiments.
- the opening 24 is a draw-in 30 upward, as shown in FIG. 5, a feeder 30 downwards, as shown in FIG 6, in each case on the outside, as shown in FIGS. 5 and 6, or a feeder 30 downwardly in the area of the flow opening 2 of the dip tube 1 1 in accordance with the illustration in Fig. 7.
- the dip tube 11 with a In the embodiment shown in FIG.
- the dip tube has a flow region at the end of the flow opening 12 Absetz 32 on and by means of the offset 32 and a sealing ring 33 arranged between the offset 32 and the deflection plate 24, the dip tube 11 is indirectly by means of the D ichtringes 33 on the deflection plate 24.
- the dip tube 1 1 is soldered by means of an annular disc 34 on the deflection plate 24. At a Such, latter soldering is thus a fixed bearing 15 between the dip tube 1 1 and the deflection plate 24 before.
- coolant for. As water with an antifreeze or air, passed as a second fluid to the batteries. At the batteries, the coolant absorbs heat from the batteries and is then passed in a circuit to the heat exchanger 1.
- the cooling center! flows through the second fluid channel of the heat exchanger 1
- the refrigerant of the refrigerant circuit with a not dargesteliten compressor and a condenser also flows through the heat exchanger 1, that are considered in total by the first fluid channel of the heat exchanger 1 with the heat exchanger 1 according to the invention as an evaporator or refrigerant evaporator significant benefits.
- the first enclosure opening 6 and the first outlet opening 7 for introducing and discharging the refrigerant into and out of the refrigerant evaporator 1 are formed on one side of the stack 3 and the rest of the heat exchanger 1, because with the dip tube 11, the refrigerant from the cover plate. 9 is passed to the first fluid channel.
- Fixation device for fixing the heat transfer 'holes in fixation
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Manufacturing & Machinery (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Electrochemistry (AREA)
- General Chemical & Material Sciences (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201110008653 DE102011008653A1 (de) | 2011-01-14 | 2011-01-14 | Wärmeübertrager |
PCT/EP2012/050529 WO2012095531A1 (de) | 2011-01-14 | 2012-01-13 | Wärmeübertrager |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2663823A1 true EP2663823A1 (de) | 2013-11-20 |
EP2663823B1 EP2663823B1 (de) | 2017-03-15 |
Family
ID=45497994
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12700478.6A Active EP2663823B1 (de) | 2011-01-14 | 2012-01-13 | Wärmeübertrager |
Country Status (5)
Country | Link |
---|---|
US (1) | US9093729B2 (de) |
EP (1) | EP2663823B1 (de) |
CN (1) | CN103328914B (de) |
DE (1) | DE102011008653A1 (de) |
WO (1) | WO2012095531A1 (de) |
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EP3540352A4 (de) * | 2016-11-09 | 2020-06-24 | Hangzhou Sanhua Research Institute Co., Ltd. | Fluidwärmeaustauschanordnung und wärmeverwaltungsystem eines fahrzeugs |
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-
2011
- 2011-01-14 DE DE201110008653 patent/DE102011008653A1/de not_active Ceased
-
2012
- 2012-01-13 US US13/979,473 patent/US9093729B2/en active Active
- 2012-01-13 WO PCT/EP2012/050529 patent/WO2012095531A1/de active Application Filing
- 2012-01-13 CN CN201280005306.5A patent/CN103328914B/zh active Active
- 2012-01-13 EP EP12700478.6A patent/EP2663823B1/de active Active
Cited By (1)
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EP3540352A4 (de) * | 2016-11-09 | 2020-06-24 | Hangzhou Sanhua Research Institute Co., Ltd. | Fluidwärmeaustauschanordnung und wärmeverwaltungsystem eines fahrzeugs |
Also Published As
Publication number | Publication date |
---|---|
US20140013787A1 (en) | 2014-01-16 |
CN103328914A (zh) | 2013-09-25 |
DE102011008653A1 (de) | 2012-07-19 |
CN103328914B (zh) | 2016-05-25 |
US9093729B2 (en) | 2015-07-28 |
WO2012095531A1 (de) | 2012-07-19 |
EP2663823B1 (de) | 2017-03-15 |
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